Excavator



May`2, 1944. `YR1 E i HoATE Erm.

EXCAVATOR Filed Sept, 2l, 1940 9 Sheets-Sheet 1 new mi? 0.

MM M P/ 5% May 2,l 1944- R. E.fcHoATE ETAL ExcAvAToR Fil'ed sep. 21

1940 9 Sheets-Shes?l 2 May 2, 1944.

R. E. HoATE ET Al.

EXCAVATOR 9 sheets-sheet 3 Filed Sept. 2l, 1940 INVENTORS l og f. Choa/e y t BY f//S war/V7 h/'L/S//H maz@ May`2, 1944'. R. E. cHoATE ET AL EXCAVATOR Filed Sept. 2l. 1940 9 Sheets-Sheet 6 S w@ SS May 2, 1944- R. E. cHoATE ET AL 2,347,882

EXCAVATOR x Filed Sept. v21, 1940 9 Sheets-Sheet '7 WMM May 2, 1944l R. E. cHoATE ET A1. 2,347,882

EXCAVATOR Filed Sept. 2l, 1940 9 Sheets-Sheet 8 WMM May 2, 1944. R. E. cHoATE UAL 2,347,882

ExcAvAToR Filed sept. 21, 1940 9 vsheets-smet 9 Patented\May 2, 1944 UNITED STATES PATENT oFFlog EXoAvAron Roy E. Choate and Ellsworth W. Austin, Cedar Rapids, Iowa, assignors to La Plant-Choate Manufacturing Company, Incorporated, Cedar Rapids, Iowa, a corporation ci.' Delaware Application september 21, 1940, serial Nefssimz 7 Claims.

Our invention relates to means for excavating, transporting, discharging ald levelling earth or comparable material, ofthe type shown generally in Austin application Serial No. 299,299, filed October 13, 1939, and entitled Excavaton now times, especially during actual digging, if power is scant, an additional tractor is brought up behind the excavator and acts as a temporary pusher or booster. This arrangement is feasible where extra operators and equipment are available and where there is a good deal of room`f0r maneuvering. There is -no satisfactory reversing action available, hwever, and even if the tractor is operated in the very slow speed reverse, steering is diflicult partly because of the type of draft' hitch employed. In long haul operations, this is of little importance, but in short haul operations, the time spent turning around at the end of the digging trip and at the end of the return: trip may amount to ten or twenty percent of the total time. An excavator whichgcan'be operated and accurately steered at high speed in reverse is ob.- viously advantageous in this type of work.

The power requirements of a vehicle ofthis type are very severe. On relatively long hauls a representative size of excavator will carry about thirty cubic yards of material about forty miles per hour. This is accomplished with the vehicle going rapidly with respect to the engine. During excavating, a deep cut in hard material may require the full engine power at maximum engine speed yet at'a very low vehicle speed. A number of different gear ratios are advisable, but changes from one ratio to another` should be made almost instantly to avoid loss of momentum. Hence an y Another object of our invention is to provide an excavator in which the drive from the powerplant tothe wheels is generally positive yet which (Cl. S7-126) is suiciently flexible to permit ready maneuvermg. l

Another object of our invention is to provide an excavator which can be-drivenin a reverse direction for maneuvering in cramped quarters. A further object of our invention is to provide an lexcavator which is largely automatic in op-` eration so that asingle operator can handle large loads at very high speed. Another object o! our invention is to provide a excavator inl which the amount of excavation is automatically regulated for maximum perform-V ance of the vehicle.

The foregoing andfothenobjects are attained in I the embodiment of th e invention illustrateddn the drawings, in which Fig. 1 is a side elevation of an `excavator constructed in accordance with our invention;

- Fig.` 2 is a plan of the excavator shown in 20 Fig. 1:

Fig. 3 is a cross-section the planes of which are indicated by the lines 3-f-3 of Fig. 2;

Fig-4 is a cross-section the planes of which are inicated by the line 4-4 of Fig. 3;

Fig. 5 is a cross-section the plane of whichis indicated by the line 5-5 of Fig. 4; l

Fig, 6 is a cross-section the plane of which is indicated by the line 6-6 of Fig. 4;

Fig. 7 is a plan, portions of the enclosing casing being removed, of the rear portion of our excavator;

Fig; 8 is a side elevation of a motor vehicle preferably for use with our excavator;

Fig. 9 is a diagrammatic plan of the cable arrangement of our excavator;

. Fig. 10 is a schematic diagram of the controls 7 In its preferred form, our excavator includes v a main frame and main bowl structure the ele-- ments of which are articulated for relative motion about a. transverse axis and which are provided-with means for controlling such motion.

Each of the elements is supported on groundengaging wheels, the rear pair Vof which are driven by an associated source of power, and the front pair of which not only are-steerable Ibut are driven from their own associated source of power. The sources of power` are under the control of the vehicle operator and transmit their driving force through hydraulic couplings and automatically shiftable ratio-changing transmis- SiQnS responsive to the speed orthe respective j ing position 'as shown in Fig'.

'which is mounted for relative rotation differentials. The earth-handling devices, v'that A i l vassesses driven ',wheels. The drive 'is also` transmitted.`

' In order to eiiectuate relative steering rotation between the main frame mast 33 and the steeris, the' main com, thepusher 'and the auxiliary bowl, are power-actuated by operator-controlled cable-winches and hydraulic cylinders.

The excavator structure is supported upon apair of rear ground-engaging wheels I2 and a pair of front ground-engaging wheels I3' and is made up of a rear, main bowl section |4 articulated to a front. main frame section I6 for rela-' tive rotation about'a transverse horizontal axis |1. Relative rotation about the axis is controlled by double -ating hydraulic piston and cylinder structures |8 pivotally mounted on the frame I6 and connected through stopped bell-cranks I9 to the main bowl section |4. Thevarious instrumentalities within and associated with the main bowl, including the bell-cranks I3, are substantially as shown in the above-identified Austin application. These instrumentalitiesgenerally comprise connected by an articulation 22 to an earth-retaining member 23 or auxiliary bowl or front tion of the `pusher 2| the front apron 23 closes.

While thefront apron is open, material is either discharged from or loaded into the main bowl over a cutting edge 26 disposed approximately midway oi the length of the main bowl structure. Upon appropriate operation of the hydraulic cylinders I8, the cutting edge 28 can be raised to its carry- 1, or can be lowered therefrom to a maximum cutting position below the surface. of the ground, such-movement being accompanied byrelative rotation of the main bowl section |4 with respect rto the main frame section I8 about the transverse axis I1 and also about the rotational axes of thel and the front wheels I3. When the hydraulic cylinders I3L are not actuated, but the liquid is blocked therein, lthey function as restraining or locking means to prevent unwanted -or erratic relative .rotation of the main bowll and 4main frame members, 'thereby preserving the selected the operator;

The forward connected toand includes a steering member 3| spect tolthe main frame about a vertical a and since the 'front wheels I3 are connec ythe steering member there is thus provided a means for effectuating steering movement of the entire vehicle, the extent of steering motion of the front wheels being a rotation of substantially 90 degrees in either direction from the straightahead positiongso that the vehicle can be steered 'with its front wheels traveling in a directionjat right angles to the direction oflthe rear wheels. 'I'his 4permits very abrupt turning and sharp maneuvering of the lv'ehicle in cramped. quarters.-

The steering member 3| is primarily a hollow casing having (Fig'. 5) a vking pin.34 ther-ein also mounted within ,a central mast 33 forming part of .the main frame.

The king pin 34 is extended to form a pivot connection with a knuckle frame 38' preferably integral with the steering member rear wheels I2 V portion of the main frame I3 is f with relan earth dischargeor pusher` member `2 I which is translatable within the main ixiwl |4 and which is ingmember 3|, the-e is vmounted on the casing 3| within a steering compartment 31 a bevel ring gear 38 with which meshes (Fig. 6) a steering bevel 33 journaled on a collar 4| and also meshing vwith a bevel ring gear 42 within the compartment and fast on the mast 33. .An extension 43 of the collar 4| forms a' pivotal mounting for' a piston rod 44 of a hydraulic steering 'structure (Fig. '4). A double-acting steering cylinder 41 is at one end mounted on a pivot pin 49 fast with respect to the steering member 3| and disposed on an extended bracket 5| materially' spaced from the king pin 32.

Upon appropriate control of oil ow to and from the chambers of the cylinder 41, the piston rod 44 is advanced or retracted to rotate the extension 43 and to mov'ethe bevel 33, so that relative rotation takes place between the ring gears 38 and 42, thus,producing relative rotation between the steering member 3| and the mast 33 of the main frame. The gear `reduction employed is at a ratio of two to one, so that, for 90 degrees angular motion of the extension 43, 180 degrees angular motion of the steering member with respect to the steering mast 31 is provided. Also by use of this mechanism, and because of the resistance to iiow of ized, the steering member 3|, despite extraneous shocks, remains substantially in the'selected position, although the operator can, if desired, permit some seepage or leakage in order that a-dashpot eilect may be provided. l

Steering movement is' imparted from the steering member 3| to the front ground-engaging lel rods 53 serving as pivotal mountings for a pair levers' 51 and 58. Thus,

of support levers 51 and 58 fulcrumed on the steering member at their inner ends and at their outer ends vconnecteciby parallel pivots/59 and 3| to the enlarged plate end |i2v of an axle tube 83. On the axle tube are disposed bearings and 35 rotatably supporting a wheel 83 provided .withl detachable connectors 61 securing it to a rim 68 on which'aground-engaging pneumatic tire 33 and wheel unit revolve yupon the axle 4tube 33,

with respect to the steering member 3| as permitted by the rising and falling movement of the the steering member about the 'central vertical axis 32 is accompanied by a corresponding movement of the wheels in unison therewith, to accommplish steering of-the excavator while rising Il ing wheels can acco andialling movement of thewheels to accommodate for -lreguiarmes in theground is permitted. This accommodation is resiliently restrained. Interposed between pads on the steering memb'er'3l and pads on the plate 32 is a pair of coil, springs 1| for transmitting the weight of the vehicle to the ground-engaging wheels. An- .other pairof springs is symmetrically arranged, and with this suspension arrangement the steering axis 32 may remain substantially in a vertical position while eith of the front ground-engagodate itself to irregularithe-hydraulic uuid ualrotational movement of but likewise the wheel assembly rises and fails steering member 3|.

ties in` the terrain independently of similar a'ccommodating movements by the other wheel. A In order to provide a support for the operators station and for propulsion mechanism, thevsteering knuckle frame 36, approximately midway of itsv height, is extended to provide a substantially horizontal beam platform 16 which forms the floor of an operators cab 11 containing a seat ,18 for the operator and a steering wheel 19, together with other control instrumentalities, and from which the operator can see not onlyo ahead but also behind into the earth-'excavating structure, for full visual observation of the entire operation.

Situated beneath and partially supported by the oor beam 16 is a source of power, such asan internal combustion engine 8|'. This powerplant is peculiar or individual to the front/ ground-engaging wheels which are driven thereby, and furnishes substantially half of the total power supplied to the-vehicle. The engine is preferably Water-cooled, with the radiator structure 82 forming a link to assist in supporting the engine, and derives fuel from a tank 83idisposed beneath the drivers seat 18. The engine 8| not only supplies power directly to the vehicle butalso has a power take-olf housing 84 from which a shaft 86 projects to drive an air-pump 81 tosupply compressed air for operating various instrumentalities and likewise to drive a hydraulic or oil pump .88 for operating other instrumentalities. l

'I'he engine itself terminates in a standard bell housing 89 in which the engine crank-shaft 9| is journaled and which bolts to a housing 93 for a hydraulic coupling. This comprises a toroidal drive member 94 operating on and with the crankshaft 9| and driving, by hydraulic connection, a toroidal driven member 96 mounted on a driven shaft 91 extending "to a reversing mechanism, generally designated 9 8, contained within a housing 99. Ihis housing is preferably bolted to the coupling housing 93 and to a receiving face on the i We prefer that the reversing gear be capable of driving the Vehicle in either direction at` maximum speed and power so that the excavator no t only can advance at maximum rate into a narnals within the housing 3|. With thisl arrangement, when the disc |0| is in neutral position, no power is transmitted from the driven shaft 91 to the shaft |06. When the disc |0| isin frictional engagement with the disc |03, power is transmitted directly to the shaft |06 and turnsit in the same direction as the engine crank-shaft 9| ro'- tates. When, however, the disc |0| is in contact with the disc |04, this latter disc then rotates in the same direction as the engine crank-shaft, but this direction of rotation is reversed through the pinion 'gears |09, so that the gear |01 and the shaft |06 are thenrotated in a direction opposite to the direction of rotationl of the crank-shaft 9|. There is, however, no speed change by means of this reverse gear transmission, so that there is provided either a complete neutral disconnection or full power transmission in either of two opposite directions. This is all under the control of the shifting fork |02 which is itself controlled by the vehicle operator.

In addition to the reversing mechanism,` we provide a ratio-changing mechanism between the source of power and the ground-engaging wheels, and this preferably takes the form of a spurgear transmission located in a casing I bolted on the rear ofthe steering member 3| and also forming y a support for the bracket 5| previously described.

Any suitable ratio-changing mechanism can be utilized, and any desired number of ratios can be afforded, but for example herein we have disclosed an arrangementwhich is under the control of the operator or which is automatically actuated and provides a choice of any one of eight speeds or ratios. This, in conjunction with the revers- .ing mechanism, affords eight speeds rearwardlyA and eight speeds forwardly between the engine and the ground-engaging wheels.

In the ratio-changing transmission the transmission shaft |06 carries a'. driving dog clutch ||2 nnder the cont-rol of a shifting fork I3 and movable from a neutral position into either of two extreme positions in enga-gement either with a Y. gear I4 or with a gear ||6.` Each of these gears row cut, for example, but can also retract, from such a cut and thus perform a maneuver which cannot be performed by present excavating structures. For that reason, the reversing mechanism l vrtakes the -form of 'a driving disc |0| which has a middle,l neutral position, as shown in Fig. 5, and may be shifted by a shifting fork |02 in either l any large difference in speed being gradually absorbed by the hydraulic coupling 93.

The' driven member |03 is connected directly to a transmission shaft |06 which extends through the steering housing 3| and which carries a bevel side gear |01. The'driven member |04, however,

is connected to a bevel side gear los. Together these are freely rotatable withrespect to the shaft |06, yet the gear |08 is connected with the bevel gear |01 through pinion gears |09 restrained against planetary rotation and mounted in jouris freely rotatablev upon the shaft |06 until it is coupled thereto by the dog clutch |2 upon'operation of the shifting fork ||3. Meshing with the gears is a pair of cluster gears ||1 and |I8, respectively, which are fast on a countershaft ||9. Also fast on this shaft is a second shifting dog 'clutch |2| under thecontrol of a shifting fark, |22, so that upon operation of the fork the clutch` |,2I couples to the countershaft ||9 either of two ing forks ||3, |22 and |38, each of which has two shifted positions with a different gear ratio effective in each, by appropriatelyshiftingthese forks-`-`r a'total of eight different ratios is obtainable.

After the speed ratio has been established in the transmission casing the drive is taken from the shaftn|31rthrough a pinion |38 meshing with a ring drive gear |39 mounted on a differential spider |4| journaled within the steering member 3| Differential pinions |42 are carried by the spider |4| .and mesh with side gears |43 and |44. Ordinarily, the drive from the ring gear |39 is trated in the remaining figures, they are diagrammatically shown in their functional relationship in Fig. 10. A

Preferably. all of the control irlstrumentalitiesV are arranged within convenient operating distance of the operator stationed within the cab 11 and are connected as diagrammatically illus; trated in Fig. 10. To control the power output of the front. engine 8| there is provided a throttle or governor controller 25| constituted by an operating handle connected by linkage 252 to the spring 253 of an engine governor 254. By varying the.tension of the spring, the effect of the governor 254 on the fuel supplier 256 of the engine 8| is varied. Thus, for any given or set position of the lever 25|, the engine is automatically maintained by the governor 254 at substantially the established level of output. Similarly, and arranged in very close juxtaposition to the lever 25|, is a controller 251 which is connected'by linkage 258 to the speed governor 259 ofthe engine |16, the governor being likewise connected by a rod 260 to the fuel supplier 26| of that engine. Since the levers 251 and 25|. are arranged close together, they either can be simultaneously operated as a unit by the vehicle operator so as to produce identical changes in operating characteristics of both engines, or can be individually operated for different poweroutput from each` engine.

For usual operation of the vehicle, the controllers 25| and 251 are operated together and uniformly, so that both engines 8| and |16 produce substantially equivalent amounts of power and produce substantially equal torques at the driving wheels. In this type of operation the engine 8|, in propelling the vehicle forward, prov duces a torque reaction which tends to move the forward portion of the main frame in a counterclockwise direction (Fig. 3) about the axis of the front ground-engaging wheels, whereas the rear engine |16 produces a driving torque reaction which tends to rotate the rear portion of the main frame and'main bowl structure also in a counter-clockwise direction (from the 'same viewpoint) about the axis of the rear wheels. These ltorque reactions, being exactly equal, neutralize mally resisted by the hydraulic cylinder mecha:

nisms I8. Since these are under the control of the operator, the torque reactions can be utilized for relatively rotating the parts of the structure. The individual controls for the Aengines are .particularly valuable in operating lthe vehicle where very sharp turns are made and especially where the terrain is exceedingly rugged and contains chuck holes or mud holes, since, by selective application of the motive power, advantage may be taken of the most favorable traction. But for all ordinary purposes under reasonably favorable conditions, both of the controllers 25| and 251 are operated in strict conjunction.

For controlling the steering of the vehicle, the operator is provided with the steering wheel 18 which is connected through a resilient means,

lower valve 263. This follower valve controls the flow of hydraulic fluid through conduits 264 and 266 to opposite ends of the cylinder 41, so that as the steering wheel 19 is turned,'the follower valve 263 produces an equivalent displacement of the cylinder and, correspondingly, an equivalent turning of .the ground-engaging wheels. The wheels consequently are turned by power and are held in positions at all times corresponding to the turned position of the steering wheel.

To supply-not only the cylinder 41 but likewise the other hydraulic instrumentalities with a supply of hydraulic fluid, the pump 88 ha its intake 261 extending to a tank 268 and discharges through an outlet conduit 269. A by-pass check valve'21l regulates the pressure within the out- 'let conduit, returning any excess of uid to the tank 268. A follower valve pressure pipe 212 extends through a flexible connection 213 to the follower valve and supplies appropriate chambers Within the valve with pressure fluid. A 'return flexible conduit 214 is connected to a return pipe 216 extending to the tank 268. The port arrangement within the follower valve is such that, as the valve is moved in response to the steering wheel rotation, the pressure iiuid is communicated through the valve body 211 to the appropriate portion of the cylinder 48, so thatfo any degree of steering wheel rotation the front wheels are steered an equivalent amount through .the intervening servo action of the follower valve and the hydraulically actuated cylinder..

Since the steering of the vehicle is of the central pivot or fifth wheel type, it is deemed desirable progressively to limit the amount of turning angle with increasing speed, so that, Iwhile the vehicle is fully maneuverable when it is operating at low speed and in cramped quarters, the amount of turning which can be effected at higher speeds is progressively decreased as the vehicle speed increases. Since the excavator is intended to haul very heavy loads of earth at a relatively high rate of speed, an automatic means is provided for insuring stability by precluding excessive steering movement; that is, by reducing the range of possible steering as the speed is increased.

For this reason, there is driven by the rear wheels l2, or is responsive to the speed thereof, an excavator speed governor 216 -which translates a controller 219 as the vehicle speed -increases. The movement of this controller is likewise transmitted through a'similar control rod 28| fastened thereto and effective through a link 282 to translate a restraining block 283 against |the urgency of a return spring 284. The block has a cam face 286 which is contoured to cooperate with a cam 281 moving simultaneously with and fast upon the follower valve 263. When the parts are in the position shown in Fig. 10, which is the low-speed position-there is no restriction whatsoever upon lthe transverse translatory movement of the cam 281, and full steering may be obtained. But as the speed of the vehicle increases, the `governor 218 actuates the control rods 219 and 28| and, through the connection 282, tensions the spring 284 lby translating the .block 283 toward the cam 281. When that is done, the cam face 286 progressively limits the translatory movement'of the cam, and when the cam blockis fully in contact with the cam 281 the translatory movement thereof is limited to a predetermined amount-for example, 30 desuch as a spring 262, with-a bodily movable folgrees of steering of the front wheels each side of center position. y Since the steering wheel 19 is connected to the follower valve 263 by means of a resilient connecting spring 262, even if the operator should operate the wheel 'I9 beyond the permissible 30- degree limit at high speed, for example,` the cam block 283, being actuated` by a superior force, will restore the lcam 281 and the follower valve 283 toward central position sufilciently to bring the steering within the established maximum range at that speed. Thus, while steering is entirely free at relatively low speeds and is restricted to a predetermined maximum amount at high speeds, the range of restriction gradually varies between the low-speed and high-speed limits as the cam 281 is contacted 4by successive portions of the cam face 286. This mechanism provides an automatically effective means for precluding dangerous steering at the higher speeds.

Arranged for convenience ne'Xt to the steeringv wheel 19 is a controller 29| which is eective to rotate a conventionally illustrated hydraulic valve 292 for controlling the supplyof hydraulic fluid through the supply pipe 269 to the cylinders I8 connected in parallel, and the discharge of fluid l therefrom through the discharge pipe 218. These are the cylinders which determine the resistance of the mechanism to torque reactions of the engines when driving and also govern the position of the cutting edge 26. By appropriately operating the controller 29| the operator can admit, release or hold hydraulic fluid within the cylinders I8 to retain'the parts locked in position y or to move the parts to any selected other position `within the total range of movement.

While many other control instrumentalities on the excavator can be hydraulically actuated, it is -preferred, in the present embodiment, to utilize hydraulic actuation only for the steering and for the cylinders I8. The remaining power-operated i instrumentalities are preferably operated through the medium of compressed air. Thus, the compressor 81; driven by the forward engine 8l, supplies air under a predetermined regulated pressure to a tank 30|. From the tank a pressure line 302 extends to valves 303 and 304 which control the brakes on the front wheels and on the rear,d wheels, respectively. The valves 303 and 304 are provided with individual pedals 300 and 301 located side by side and convenient to the driverin the operators cab, so that the front end of the device may be .braked separately from the v rear end. The braking produces torque reactions quite similar to those produced by the engine driving forces, except that they occur in a reverse direction and, unless exactly equal (in which case they neutralize), are also resisted by the double-acting hydraulic chambers I0. While .ordinarily the operator controls both of the pedals 303 and 301 in unison, this being facilitated by their location in juxtaposition, the operator can, since the brake pedals are separate, individuallycontrol -the brakes to facilitate maneuvering of the vehicle.

In accordance with our invention, and in order to assist .in the versatility and maneuverability of the'vehicle, we provide means for permitting the differential mechanisms, such as MI, normally to function' when the vehicle is turning a subated to establish connection between the' branch.

308` and an air line 3| I extending to an operating chamber 3I2 connected to the lever ISI for operating the locking clutch on the front difierential. 'I'he branch 308 likewise extends to a control valve 3I3 normally ineffective but, when ac; tuated, effective to establish communication" through a line 3M to an operating chamber 3I0 of a similar character but working upon the locking clutch lever for the differential of the rear engine.

A Thus, when the valve 309 is operated, the air pressure is eifective to unlock the front differential,.whereas when the valve 3I3 is actuated, the air pressure is effective to unlock the .rear diff ferential. The differential locking and unlockingeis preferably responsive to steering movement.

Consequently; moving in conjunction with the steering piston rod 44 there is a cam block 3I1 which has\a narrow notch all on one face, ineffective when the steering is straight ahead, but effective upon a turn, of approximately 5 degrees, either side of center, to translate the valve 300. Thus, while the front differential is locked for all steering positions of' the front wheels between 5 degrees left of center and 5 degrees right of center, as soon as this amount of vturning is exceeded, the front dierential is unlocked and the drive ,of the front engine is distributed to the two front wheels. The rear differential, however, remains locked until the front steering approaches a value approximately 30 degrees either side of center, as governed by a wide cam notch 3I9 also in the block`3l1, which is effective to displace the controller 3I3. For a/ll values of steering, therefore,

substantially in excess of 30 degrees left or right of straight-ahead position, the `rear differential isunlocked and the rear wheels'are fully differentiated, or the power of the rear engine is then distributed to the two rear wheels in varying Upon restoration of the steering mechf amounts. l anism toward center position, the rear differential is relocked as soon as the range between 30 degrees left of center and 30 degrees right of center is entered, while as soon as the range bewhen energized to position a cam 320 in the path of a cam-325 mounted on the control rod 230 of the rear engine. When the front wheels are steered more than 30 degrees either side of censtantial amount, but to render the differentials inoperative or toA disable them when the vehicle is going in a straight path or approximately so. Further, we preferably arrange matters so that the front diierential mechanism and therese" ter, the controller 3I5 progressively reducesthe rear engine speed.

Conveniently arranged next to the control lever 29| for raising and lowering the cutting edge, are the winch control levers. For example, a control lever 32| is effective upon a conventional valve 322 to govern the flow from a supply pipe 323'to either of the opposite ends of an actuating cham'- ber 324 which is of a standard type repeatedly utilized in the structure and -normally centralized to a neutral position by equally acting springs example drum |9I.

ard valve 332 for regulating the supply and discharge of airvto .and from the opposite ends of j stantially uncoupled by the hydraulic coupling, so 745.

an actuating chamber 333 which vis eectiveto control operation of the winch drum |96, so that by operationr of the grouped levers 23|, 32|v and 33|, the .operator can effectuate -all-of the usual controlling motions of the'earth-carrying and handling structure.

Since the vehicle is designed to be operated as rapidly in a reverse direction as it is in forward direction, to obviate the necessity of turning around, the control of the reversing .clutch-| for the front engine and of. the corresponding clutch for the rear engine is simultaneously effe'ctuated. A reversing lever 334 controls a standard valve 336 to provide any one of three positionsthereof. In an intermediate, neutral position, air from the main 323 is excluded from a front operating-chamber 3,31 as well as from a When the valve322 is maintained in a reverse direction rear operating chamber 338. The piston in each of these chambers is spring-centralized, as pre-l viously described, when no air pressure is exerted thereupon. The chamber 331, for example, is effective to hold the shifting fork |02 of the front reversing structure in neutral position, as sh'wn inFig. 5. The chamber 338 for the rear struc ture is identical in operation,

When, therefore, the lever 334 is moved in one direction out of central position, airis admitted to lone end of both of the operatingchambers 331 and 338, and the shifting forks are effective to connect the structure for motion in one direction, for example forwardly. When the control lever 334-is shifted to its opposite extreme position, the air is released from the previously charged end `of the operating'chambers 331 and 333 and pressure air is simultaneously introduced into vthe opposite ends thereof so that the shifting forks controlled thereby are simultaneously shifted into opposite extreme positions and a reverse coupling or direction of drive is eiectuthat the remaining mechanism may be operated Without affecting the one engine.

For example, when the front wheels are turned substantially at 90 degrees to the longitudinal direction of the vehicle, the rear engine can be idle and the front engine can be operated at considerable speed and power output so as to be coupled with thefront wheels. The front drive can then be alternated between-forward and reverse, to move the forward en d of the vehicle in an arcuate path substantially Vabout the center of the rear wheel axis as a turning pivot. But at this time the rear engine, although being reversely and forwardly related to its ground-engaging wheels along with the front engine, is substantially ineifective upon the .rear Wheels because its low speed eectuates a hydraulic uncoupling. Under' these conditions the rear differential is also unlocked. The front end ofthe Vehicle can be operated substantially at right angles and with full power output. This is of considerable importance in maneuvering iin cramped'quarters and where the ground conditions are quite irregular. Thus, by reason of the common reverse of the two engines but of the separate control of the power output of each and the automatic uncoupling feature of the hydraulic couplings at low engine speeds, there is provided a. somewhat interrelated but extremely flexible and maneuverable transmission system for the excavator.

The hydraulic coupling characteristics, in addition to slippage at low speeds, are of any selected power sort, and the coupling may have, turbine or torque multiplying characteristics. Thel illustration, such as Fig. 5, is diagrammatic but discloses a type in which there is very little torque multiplica- 4tion, but in which the centrifugal coupling is extremely eiective. If nomaterial torque multiplication is provided by the hydraulic coupling, we provide other means for changing the torque ratios. lIn the present instance, therefore, where the hydraulic coupling itself has very little torque changing characteristic, we provide the eightspeed transmission or some equivalent gearchange mechanism which ispreferablyjpartly automatic and partly`under the control of the vehicle operator.

ated. Thus, vthe direction ofA advance of the -vehicle is under the control of the operator by a gingle lever, although other`parts of the drive are quitewseparate. 3

While the reversing clutches have a slight\slip page atv very high torques, the shift due to the pneumatic controllers 331 and 3 38 is relatively Y gines, and since the engines are individually controlled through the controllers 25| and 251,.it is possible, by manually or automatically minimizing the power output of oneQengine, for example, the rear engine during very sharp turns, to drive substantially by the other or front engine alone, so

' that the direction of rotation of the rear wheels Lrelative to, each other and relative Vto the rear The particular ratio of the front transmission in the casing which is effective at anyone time is controlledby a valve shaft 34| rotatable by an operators control lever 342 or by an operating rod 343 regulated by a speed-responsive governor 344 actuated by the front ground-engaging wheels |3.. Thus the position of the shaft 34| is responsive to the'speed of the frontground-engaging Wheels. That is, the greater the speed of the front wheels I3, the more the shaft 34| is rotated from' its zero position. But it may berestrained in any selected position by the vehicle operator holding the lever 342, either by hand or with a, latching structure (not shown). If vthe lever 342'fis held, the corresponding transmission remains ,in the selected ratio, but vif thelever A342 is free then the particular ratio depends upon the front-wheel speed.A Under governor control, however, the lever does not go into zero position, but at lowest wheel speed, or stopped, the lever occupies rst speed position. Manual positioning of the lever in zero position, or neutral, is entirely possible.

In a quite similar fashion, the control rod 213 from the governor 213 which is responsive to the speed of the rear ground-engaging wheels |2, ex-

engine is not particularly material. That is, one

engine, when operating relatively slowly, is subtends to and is effegtive upon the Valve control controller 342 and is located in juxtaposition.

therewith so that the two controllers 342 and 341 can be simultaneously# actuated bythe operator,

' or can be simultaneously latched in position, or

can be individually located so that under rather unusual operating conditions the ratio of power transmission between the frontengine and the front wheels is different from the ratio of power transmission between the rear engine and the vrear wheels. Normally, however, both engines are free to transmit. power through the same or approximately the same vratio vunder automatic wheel-speed responsive control.

Since the servo mechanism for translating the position of the shaft 34| into gear positions in the front transmission is substantially the same as the servo mechanism for translating the posi- -x tion of the controlling shaft 346 into"correspond ing gear positions inthe rear transmission, a description of but one of them applies to both. 4 AFor example, air from-the main 323 is conducted annees.

the port 382 is eective, thereby duplicating .the function of the poi't 38|. In fourth position,

lthe port 354 -remains effective, the port 31| remains effective, but the port 389 is eiective as previously the port 388 was effective. In i'lfth position. the port 36| becomes effective, the port 3164 becomes effective in the fashion of they origina port ses, while port :sa is frective. In c sixth position, port 36| is effective, port 364 remains effective, but port 39| is effective. In seventh position, port 36| is effective, but port 312 then becomes effective, while port 384 is conand then occupies a second extreme position for into one extreme position, and that is what 0cwhen the valve 354 is :first rotated out of its zero position. The valve 354 likewise has av port 36| connected byaduct 362 with the opposite end of the chamber 359.

The valve 355 is provided with, alternating and spaced ports 363 and 364 which areconnected by ducts 366 and 361 joining in a pipe 368. to one end of a control chamber 369. Interspersed' ports 31| and 312 join in a duct 313 connected` to the opposite end of the control chamber 363.

The piston of this chamber is effectiv? upon the shifting fork |22.

The valve 356 is provided with a series of al- .the second four speeds. The shifting fork |22 occupies one extreme position for the first two speeds, occupies its other extreme position for the next two speeds, then the first extreme position for the subsequent pair of speeds, and finally the second extreme position for the ultimate pair of speeds. Theshifting fork is alternately moved from o ne extreme position to4 the other as the range of speeds is traversed'. Thus, in response to the positionof 'the shaft`34l, the ratio of speeds between the front engine and the vfront ground-engaging .wheels is automatically or manually controlled. Since the controlling structure for the rear ratio-c anging transmission is identical, the position the shaft 346 similarly controls the ratio between the rear engine and the rear ground-engaging wheels, either automatically or manually.

Particularly under favorable or normal operatting conditions, the speed transmissions and 'hy- .-draulic couplings provide an automatic connecternate ports 38|, 382, 383 and`384, each of which is joined by its individual pipe to a duct 386 extending toone end of a controller 381 effective upon the shifting 4fork |3|. The valve. 356 intermediate each ofthe ports 38h-A382, 383 ,and 384, is provided with a series of ports '388,

- 389, 39| and 392 each of which is connected by its individual pipe to a duct 393. extending to the opposite end` of the controller 381.

Since the c ratio-changing transmission has eight speeds,'the control shaft 34| has nine positions. The initial orrzero position is illustrated in Fig. v10 in which none of the valves is in a position to supply air xand all of the'control chambers359, 369 and 381 are in neutral posi.

tion between the engines and the remaining drivv ing structure, s o that the'operator of our excavator need concern himself primarily with but the steering, braking and throttle controls 261 and 25|. He therefore can give plenty of attention to and has adequate time to operate the winch and hydraulic elevating structures of the earth-carrying portion of the machine. 'He is precluded from steering excessively at relatively high speeds and is given the assistanceof maximum driveand traction .by virtue of the locking diierentials under most conditions. vUnder extreme conditions, however, the manual controls are available for producing individual driving effects, so, that the full capabilities of the exv cavator can be obtained.

g .Under extreme operating conditions, or in certain environments, it is advisable to have an auxiliary power structure, and we have therefore tion with the various shifting forks ||3, |22 and ,i

|3|l likewise in neutral position `so that none of the gears is in power-transmittingk position.

When, however,` the shaft 34| is moved into its first position, air pressure is transmitted through the port 351, through the port 363, and through the port 38|.. simultaneously, in order to establish corresponding positions of the control chambers and the respective shifting forks. When the shaft 34| is moved to its second position, the ports 351v and 363 remain effec'- tive, but the port 388 becomes effective. In the third position, while the port 351 is still eiiective, the port 31| then becomes effective and illustrated in Fig.l 8 a device which is substantially the same as previously described in all respects except that the main frame structure 48| is not articulated between its ends and is not provided with any earth-handling structure but rather extends simply, as' a frame to a rigid connection 'at 462 with the rear engine unit. This vehicle is preferably providedvwith a rear hook 4||3 for facilitating a draft connection with the front end of the excavating vehicle shown in the remaining gures.

Under some operating conditions it is considered advisable to provide means for regulating the position of the main bowl I4 with respect to the ground, especially during cutting or excavating, in accordance with the load as represented by the speed of advance of the vehicle. That is,

hicle. This is eectuated automatically, al-4 though manual supervision is retained.4

Conversely, ifthe going is particularly easy, the cutting depth can be increased without re- .ducing the speed of advance of the vehicle, and

under those circumstances we provide a/mechanism which automatically will increase the depth of cutv so as to ensure that under all circumstances the vehicle is making the best use of the maximum power available from the power source. Most of the time the manual supervision can be omitted and the automatic mechanism relied upon, but there are often unusual circumstances which can best be met by manually controlled means.

Since this arrangement can be applied to or omitted from the mechanism without substantially altering the remaining portions thereof, it is shown in a separate diagram in Fig. 1l, it being understood that this structure preferably is added to the structure as diagrammatically illustrated in Fig. 10. As illustrated in Fig. 11, the main bowl Id is movable vertically with respectto the main frame it, in order to move the cutting edge with respect to the ground, and this motion is preferably eiectuated by the cylinder and piston arrangement i8 which is connected to the main bowl It by a piston rod dll and which is hydraulically operated.

'I'he hydraulic liquid is obtained fromthe storage tank 268 from which it is conducted through the pipe 261 to the force pump 88 and is'discharged therefrom under pressure through conduit 269 past the by-pass valve 2H and into the controlling valve 292 through the pipe 212. From the valve 292, which is operated by the hand controller 29|, discharge either is through a pipe M2 into a duct M3 leading to the bottom of the cylinder I8 and which when connected is edective to lift the piston yrod gli and correspondingly to raise the main bowl ld, or, in the alternative, is through a duct I6 into a pipe M1 leading to the top of the cylinder I8 and edective to depress thev main bowl I4 with respect to the ground. Thus, by operating the hand control 29|, as previously described, the operator may, by hydraulic power, raise and lower the main bowl It not only with respect to the main frame i6 but also with respect to the ground.

In order to provide an automatically effective means, we preferably provide a second control valve 62| arranged generally in parallel with the valve 292. The construction of the valve d2| is like that of the valve 2S2and hence it receives iluid under pressure from the duct 272 through a branch duct $22 and is shnilarly connected. to the discharge pipe 21d by a branch discharge pipe 622. In a comparable fashion the valve 22| is connected to raise the main bowl le by supplying fluid to the duct dit through a branch duct 62d, while the valve is cdnnected to lower the main bowl la by supplying iluid to the line 2| l through a branch line 62e. The control valve @2l is not provided with any manual lever but is operated by power since its operating lever d2? is ccnnected to a movable cylinder 322 within which a piston d2@ is stationarily established by a piston rod itt fastened tu a xed support Q32. 'The cylinder t28 is centralized with respect to the piston @329 by interior springs $33 and 234.

'Movement of the cylinder' t28 is preferably in response to the speed of a ground-engaging wheel, such as one of the rear wheels l2, through the medium of a s'vo or power multiplying mechanism. Rotation of the groundi-engaging wheel l2 is normally eiective through multiplying gearing 436 to drive a sensitive governor 437 at a relatively high speed. The multiplying mechanism 36 is desirable since during excavation the speed of advance of the vehicle is usually relatively slow and it is advisable, consequently, to make the -governor highly responsive during low-speed operation. The governor 3l is connected through linkage 638 to a slide valve 632 'governing the supply to and exhaust from the cylinder $38 of a pressure fluid, such as air. This air is supplied from the source through the duct 302 under the control of a valve 44| which communicates with the movable valve 439 through a exible duct M2.

The operation of the mechanism is such that, as the vehicle whel speed |2 increases, the governor 4431 correspondingly changes its position and' moves the valve 239 correspondingly. This movement displaces the valve 439 toward the right, as seen in Fig. l1, uncovering the cylinder 428 to theV left of the piston 429 to the atmosphere through a port 443 and simultaneously uncovering a port 444 in the right-hand side of the chamber 428 to the supply of pressure air through the valve 439. This produces a corresponding translation of the cylinder 42B in exact proportion to the movement of the valve 432 responsive to the governor, and the cylinder movement rotates, through the lever 427, the valve 42| so that communication is established between the supply duct 622 and the lowering duct 426, While :duid discharge also occurs from the other end of 'the cylinder 428, thereupon causing the main bowl la to lower with respect to the ground or to cause the cutting edge to engage the ground more deeply. This normally increases the load upon the veliicle and slowsv its advance to the optimum value. Y

When the speed of the vehicle is less than the optimum value and the wheel l2 drops below that speed, the governor 43'! is correspondingly affected, and the valve 439 is translated toward the left in Fig. 11, thereby exposing the port 4M to atmosphere and connecting the port M2 tothe supply of air, thereby displacing the movable eyiinder 42s toward the left in the ngure, rotating the valve 42| in a clockwise direction, and connecting the supply duct 422 to the raising duct 626.0 Thus, when the speed of the vehicle drops below the optimum value the main bowl Id is raised and the cutting edge is lifted with respect tothe ground, thereby normally decreasing the load upon the engine and permitting the vehicle speed to be restored.A

In accordance with the operation of this mechanism, the position of the main bowl is maintained at a value which will aiord substantially a constant speed or advance of the vehicle without operators supervision and automatically.

But since such. automatic regulation is of -value chieiiy during excavation, and since the sensitiv'e governor 431 may be damaged by over-speeding when the vehicle is transporting a load or dumping auload, we provide means for disabling the automatic structure except during excavation. The piston rod dlt carries a collar di which moves with such rod between the maximum excavating position indicated by thedotted lines 452 in Fig. 11, between the maximum raised position indicated by the dotted lines 453 in that figure, andthe intermediate position shown by the solid lines in Fig. 11 wherein the cutting edge is supposedlysubstantially flush with the surface .of the ground.

As the collar' 45| rises from the central position illustrated, wherein. the cutting edge is substantially even with the surface of the ground, it engages and lifts with it a lever 454 against the urgency of a springv 456, and the motion of the lever is transmittedlthrough linkage to disengage a driving clutch 458 interposed in the drive line between the rear wheels I2 and the multiplication gearing 436. Thus, as the main `bowl I4 rises above its ground-level position, the clutch 458 is disengaged and no motion is transmitted to the governor 431. Under these circumstances, in the event no manual control is exercised, the operation of the governor is such as tok produce an extreme displacement of the valve 439 sothat the valve 42| is rotated to bring the main bowl I4 to its maximum elevated position for carriage. Whenever the governor is brought to its declutched or stationary position, as, for example, when the cutting edge istrikes an obstruction, or when the load is so Y great as to slow the vehicle materially, a similar operation of the valve 439 promptly brings the bowl to highest carrying position When the main below the central position, and as the collar 45| descends, the spring 456 is effective upon the lever 454 and the linkage 451 to engage the clutch 458 and to bring the governor 431 up to speed. Below the central position, therefore, the operation is automatically controlled.

Manualcontrol by the lever 29| at all times supersedes automatic control when the operator so desires, and to effectuate that condition the lever 29| is provided with an extensioin 46| adapted to cam against a lever 462 bearing upon the endof a valve stem 463 joined to the valve 464. The valve is ordinarily pressed by a spring 466- into an uppermost position against. the lever 462 which in turn presses against the extension 46|. When the-hand control lever 29| is in its central or neutral position, so that the valve 292 is ineiective to produce any movement of the mainbowl I4, the lever 462 is depressed, as is the stem 463, against the urgency of the spring 466,y so that the'valve 464 permits free communication of-air from the duct -302 tothe valve 439 -and the servo cylinder 428. Thus, when the hand controller 29| is in a central or inactive position, the automatic mechanism can operate without restriction. But when' the hand .con-

"troller 29| is moved in either direction from its the immediate eilect is for the neutral position,

permit the lever 462 to rise with extension. I to the stem, 463 under `the urgency of thel spring 466. Simultaneously, the valve 464 rises, thereby cutting off communicatiomfrom the source of air 302 to the servo valve .439 and connecting,r 'such valve to atmosphere through a drain duct 461. Since, therefore, despite the position momentarily of the valve 439, the cylinder 428 is.

connected on4 both sides of the piston 429 to atmosphere, the centralizing springs 433 and 434 are effective instantly to restore the automatic valve 42| to a central, neutral or ineffective position, and the manual sole means of producing motion ofthe main bowl I4. As soon, however, as manualcontrol of bowl |4 is lowered to andy control lever 29I is` the ,the lever 29| 4is relinquished, or the lever is restored to its central neutral position, the valve 464 is again positioned so that the valve 439 is supplied with air and the automatic servo mechanism is restored to eiectiveness.

By the provision of this mechanism, therefore, yit is possible to have the maximum utilization of the engine power, as measured by the speed of advance of the vehicle, eiective to control the depth of cutl or, inA general, the position of the main bowl I4,although manual supervision is retained and the automatic control is made inleffective except for a portion of the range of movement of the main bowl with respect to the ground.

We claim:

wheels disposed at and supporting the rear of said structure, a rst driving engine disposed to the rear of and connected to drive said rear ground-engaging wheels, front ground-engaging wheels disposed at and supporting the front of and arranged for steering said structure, a second driving engine disposed to the iront of and connected to drive said front ground-engaging wheels., means for 'connecting said main bowl and said main frame for relative pivoting about a transverse-horizontal axis between said front and said rear ground-engaging wheels, and means for controlling the relative pivotal movement of said main bowl and said main frame about said axis.

urging said front section to rotate in one direction -about said axis, driving means for said rear wheels producing a torque reaction in said rear section urging said rear section to rotate in another direction about said axis, and means for resisting relative rotation of said sections aboutv said axis in both directions.

3. An excavator comprising a main frame and main bowl structure including a cutting edge, a member mounted therein for turning movement about a generally upright axis, two pairs of vertically spaced levers disposed one pair at each side of and'fulcrumed to said member and turnable'therewlth, said levers lying in horizontal planes whereby their outer ends may be moved vertically with respect to their fulcrums, ground wheels mounted on the outer ends of the levers of each of said pairs, and spring means for resisting the vertical movement of said levers with respect to their fulcrums whereby said wheels can yield to ground irregularities without disturbing said cutting edge.

4. An excavator comprising a vmain frame, a main bowl adapted to be moved with respect to said main frame, means connected to said main frame and to said main bowl for eiecting such movement, means for advancing said main frame and said main bowl over the ground, and means responsive to the speed of advance of said advancing means for operating said movement effecting means. n

5. An excavator comprising a main frame and A main bowl'structure, wheels for supporting said structure from the ground, an engine for driving section, means effective upon said front Wheels to 4produce a torque reaction in said front section urging said front section to rotate in one direction about said axis, means eiective upon said rear wheels to produce a torque reaction in said rear section urging said rear section to rotate in another direction about said axis,v and means for resisting relative rotation of said sections about -said axis in both directions.

7. An. excavatorcomprising a ground-supported main frame, a main bowl movable with respect to said main frame, means for so moving said main bowl, a pusher movable within said main bowl, an auxiliary bowl articulated to said pusher for conjoint movement `therewith, a winch having a pair of independently operated drums, a cable operated by one of said drums and applied directly to said pusher for moving said pusher together with said auxiliary bowl in o ne direction, and another cable operated bythe other of said. drums and applied directly to said pusher for moving said pusher together with said auxiliary bowl in the opposite direction.

ROY E; cHoA'r-E. ELLsWoRTH W. AUSTIN.A 

